Spring latching connectors radially and axially mounted

ABSTRACT

A spring latching connector includes a housing having a bore therethrough, a piston slidably received in said bore, circular groove formed in one of said bore and piston and a circular coil spring disposed in said groove for latching said piston and housing together. The groove is sized and shaped for controlling, in combination with a spring configuration, disconnect and connect forces of the spring latching connection.

The present application claims priority from provisional patentapplication Ser. No. 60/476,105 filed Jun. 4, 2003.

The present invention generally relates to connectors and is moredirectly related to the use of canted coil springs in connecting apiston and a housing for mechanical and electrical connection purposes.

The connection may used to hold or latch and disconnect or unlatch.Various types of canted coil springs, such as radial, axial, or turnangle springs may be used depending on the characteristics desired for aparticular application.

Axial springs may be RF with coils canting clockwise or F with coilscanting counterclockwise, and installed or mounted with a front angle infront or in back relative to a direction of piston travel in aninsertion movement. The springs can be mounted in various manners in agroove in either the piston or the housing. While the spring isgenerally mounted in a round piston or a round housing, the canted coilspring is capable of being utilized in non-circular applications such aselliptical, square, rectangular, or lengthwise grooves.

Various applications require differing force and force ratios for theinitial insertion force, the running force, and the force required tolatch and disconnect mating parts. The force, the degree of constraintof the spring, the spring design, the materials used, and the ability ofthe spring and housing combination to apply a scraping motion to removeoxides that may form on mating parts have been found in accordance withthe present invention to determine the electrical performance of theconnector. Electrical performance means the resistivity and theresistivity variability of the mated parts.

SUMMARY OF THE INVENTION

It has been found that the force to connect and the force to disconnectas well as the ratio between the two is determined by the position ofthe point of contact relative to the end point of the major axis of thespring when the disconnect or unlatch force is applied and thecharacteristics of the spring and the spring installation or mounting.The maximum force for a given spring occurs when the point of contact isclose to the end point of the major axis of the spring. The minimumforce for a given spring occurs when the contact point is at the maximumdistance from the end point of the major axis, which is the end point ofthe minor axis of the spring. This invention deals in part with themanner in which the end point is positioned. The material, springdesign, and method of installing the spring determine the springinfluenced performance characteristics of the invention.

Accordingly, a spring latching connector in accordance with the presentinvention generally includes a housing having a bore therethrough alongwith a piston slidably received in the bore.

A circular groove is formed in one of the bore and the piston and acircular coil spring is disposed in the groove for latching the pistonin a housing together.

Specifically, in accordance with the present invention a groove is sizedand shaped for controlling, in combination with a spring configuration,the disconnect and connect forces of the spring latching connector.

The circular coil spring preferably includes coils having a major axisand a minor axis and the circular groove includes a cavity forpositioning a point of contact in relation to an end of the coil majoraxis in order to determine the disconnect and the connect forces. Morespecifically, the groove cavity positions the point of contact proximatethe coil major axis in order to maximize the disconnect forces.Alternatively, the groove cavity may be positioned in order that thepoint of contact is proximate an end of the minor axis in order tominimize the disconnect force.

In addition, the coil height and groove width may be adjusted inaccordance with the present invention to control the disconnect andconnect forces.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention may be more clearly understood with reference tothe following detailed description in conjunction with the appendeddrawings of which:

FIG. 1 a shows a front view of a canted coil spring with the coilscanting counterclockwise as indicated by the arrow;

FIG. 1 b shows and enlarged view of the coils;

FIG. 1 c shows the position of the front and back angle;

FIG. 1 d shows the difference between the lengths of the front angle andthe back angle;

FIG. 1 e shows the position of the front and back angles;

FIG. 1 f shows a cross sectional view of a radial spring.

FIG. 2 a shows a radial spring in a flat bottom-housing groove;

FIG. 2 b shows a left side view of the spring;

FIG. 2 c shows a front view of a counterclockwise radial spring with afront angle in the front;

FIG. 2 d shows a cross sectional view of the spring;

FIG. 2 e shows a cross sectional view of the spring mounted in ahousing, a reference dot point indicating a position of a front angle ofa coil, “the end point of a major axis of the coil” being used toexplain the relationship between a point of contact and the end point ofthe major axis of the coil when determining the unlatching or disconnectforce, the dot point showing a position of the front angle of the coil;

FIGS. 3 a-3 e show a radial spring mounted clockwise in a flat bottomhousing groove with the front angle in the back, the spring having coilscanting clockwise;

FIGS. 4 a-4 e show a latching radial spring in a standard latchinggroove, housing mounted (shown in FIGS. 4 a and 4 e);

FIGS. 5 a-5 e show a radial spring axially loaded with the groovesoffset in a latched position eliminating axial play, with FIGS. 5 a and5 e showing the spring in an axial load position to eliminate axialplay, which enhances conductivity and reduces resistivity variable butincreases insertion force;

FIGS. 6 a-6 e and 7 a-7 e show the same type of design but pistonmounted. FIGS. 6 a-6 e show a latching radial spring in a latchinggroove, piston mounted, while FIGS. 7 a-7 e shows a latching radialspring with offset axial grooves for minimal axial play piston mounted.The features are the same as indicated in FIGS. 4 a-4 e and 5 a-5 eexcept piston mounted;

FIGS. 8 a-8 d show a series of circular holding multiple radial springmounted one in each groove. Each spring is separate from the others,FIGS. 8 a and 8 b showing springs being compressed radially by the shaftas it moves in the direction of the arrow, FIG. 8 c showing a crosssection of the spring and FIG. 8 d showing an enlarged view of a portionof FIG. 8 a. Springs in a multiple manner could also be axial;

FIGS. 9 a-9 d show a holding multiple radial springs mounted in multiplegrooves, this design being similar to the one indicated in FIGS. 8 a-8 dbut the grooves are physically separated from each other, springs in amultiple manner may also be axial;

FIGS. 10 a-10 d show a holding length spring mounted axially in athreaded groove, FIG. 10 b showing the piston partially engaging thehousing by deflecting the spring coils, FIG. 10 a showing the shaftmoving in the direction of the arrow with further compression of thespring coils, FIG. 10 c showing a length of the spring and FIG. 10 dshowing an axial spring mounted in the groove with two spring coilsdeflected and one not deflected as yet;

FIGS. 11 a-11 e shows a face compression axial spring retained by insideangular sidewall;

FIGS. 12 a-12 e show a latching radial spring in a radial groovedesigned for high disconnect to insertion ratio shown radially loadedand causing the coils to turn to provide axial load to reduce axialmovement. GW>CH;

FIGS. 13 a-13 e show a latching axial spring in an axial groove designedfor high disconnect to insertion ratio with the spring shown in anaxially loaded position to limit axial play, the spring coils assuming aturn angle position that increases force and provides higherconductivity with reduced variability;

FIGS. 14 a-14 k show a spring with ends threaded to form a continuousspring-ring without welding joining, which is different than the designindicated in FIG. 1;

FIGS. 15 a-15 k show a spring with end joined by a male hook andstep-down circular female end to form a continuous circular spring-ringwithout welding;

FIGS. 16 a-16 l show a spring with the coil ends connected byinterlacing the end coils to form a continuous spring-ring withoutwelding or joining;

FIGS. 17 a-17 d show a spring with coils ends butted inside the grooveforming a spring-ring without welding; and

FIGS. 18 a-18 f show an unwelded spring ring and to be housed in a flatbottom housing groove, front angle in the front, showing the variousdifferent designs that could be used to retain the spring in a groovethat can be a housing groove or a piston groove.

DETAILED DESCRIPTION

Connectors using latching applications have been described extensively,as for example, U.S. Pat. Nos. 4,974,821, 5,139,276, 5,082,390,5,545,842, 5,411,348 and others.

Groove configurations have been divided in two types: one type with aspring retained in a housing described in Tables 1a-1g and another withthe spring retained in a shaft described in Tables 2a-2g.

Definitions

A definition of terms utilized in the present application isappropriate.

Definition of a radial canted coil spring. A radial canted coil springhas its compression force perpendicular or radial to the centerline ofthe arc or ring.

Definition of axial canted coil spring. An axial canted coil spring hasits compression force parallel or axial to the centerline of the arc orring.

The spring can also assume various angular geometries, varying from 0 to90 degrees and can assume a concave or a convex position in relation tothe centerline of the spring.

Definition of concave and convex. For the purpose of this patentapplication, concave and convex are defined as follows: The positionthat a canted coil spring assumes when a radial or axial spring isassembled into a housing and positioned by-passing a piston through theID so that the ID is forward of the centerline is in a convex position.

When the spring is assembled into the piston, upon passing the pistonthrough a housing, the spring is positioned by the housing so that theOD of the spring is behind the centerline of the spring is in a convexposition.

The spring-rings can also be extended for insertion into the groove orcompressed into the groove. Extension of the spring consists of makingthe spring ID larger by stretching or gartering the ID of the spring toassume a new position when assembled into a groove or the spring canalso be made larger than the groove cavity diameter and then compressedthe groove.

Canted coil springs are available in radial and axial applications.Generally, a radial spring is assembled so that it is loaded radially.An axial spring is generally assembled into a cavity so that the radialforce is applied along the major axis of the coil, while the coils arecompressed axially and deflect axially along the minor axis of the coil.

Radial springs. Radial springs can have the coils cantingcounterclockwise (Table 1a, row 2, column 13) or clockwise (Table 1a,row 3, column 13). When the coils cant counterclockwise, the front angleis in the front (row 2, column 13). When the coils cant clockwise (Table1a, row 3, column 13), the back angle is in the front. Upon inserting apin or shaft through the inside diameter of the spring with the springmounted in the housing in a counterclockwise position (Table 1a, row 2,columns 2, 3, 5), the shaft will come in contact with the front angle ofthe coil and the force developed during insertion will be less than whencompressing the back angle from a spring in a clockwise position. Thedegree of insertion force will vary depending on various factors. Therunning force will be about the same (Table 1a, row 2, columns 6, 8).

RUNNING FORCE. Running force is the frictional force that is producedwhen a constant diameter portion of the pin is passed through thespring.

Axial springs may also be assembled into a cavity whose groove width issmaller than the coil height (Table 1a, row 5, columns 2, 3, 5, 6, 7 and8). Assembly can be done by inserting spring (Table 1a, row 5, column13) into the cavity or by taking the radial spring (Table 1a, row 7,column 13) and turning the spring coils clockwise 90° into a clockwiseaxial spring (Table 1a, row 7, column 15) and inserting into the cavity.Under such conditions, the spring will assume an axial position,provided the groove width is smaller than the coil height. Under suchconditions, the insertion and running force will be slightly higher thanwhen an axial spring is assembled into the same cavity. The reason isthat upon turning the radial spring at assembly, a higher radial forceis created, requiring a higher insertion and running force.

Axial springs RF and F definition. Axial springs can be RF (Table 1a,row 5, column 13) with the coils canting clockwise or they can be F(Table 1a, row 6, column 13) with the coils canting counterclockwise. AnRF spring is defined as one in which the spring ring has the back angleat the ID of the coils (Table 1a, row 5, column 12) with the front angleon the OD of the coils. An F spring (Table 1a, row 6, column 13) has theback angle on the OD and the front angle at the ID of the coils.

Turn angle springs are shown in Table 1e, row 10, column 13, Table 1f,rows 2-5, column 13. The springs can be made with turn angles between 0and 90 degrees. This spring can have a concave direction (Table 1a, row5, column 6) or a convex direction (Table 1a, row 5, column 8) whenassembled into the cavity, depending on the direction in which the pinis inserted. This will affect the insertion and running force.

F type axial springs always develop higher insertion and running forcesthan RF springs. The reason is that in an F spring the back angle isalways located at the OD of the spring, which produces higher forces.

Definition of Point of Contact. The point of load where the force isapplied on the coil during unlatching or disconnecting of the two matingparts. (Table 1a, row 2, column 11, row 5, column 11).

Definition of “end of the major axis of the coil.” The point at the endof the major axis of the coil. (Table 1a, row 2, column 2 and row 5,column 2).

Types of grooves that may be used.

Flat groove. (Table 1a, row 2, column 4) The simplest type of groove isone that has a flat groove with the groove width larger than the coilwidth of the spring. In such case, the force is applied radially.

‘V’ bottom groove. (Table 1a, row 4, column 4) This type of grooveretains the spring better in the cavity by reducing axial movement andincreasing the points of contact. This enhances electrical conductivityand reduces the variability of the conductivity. The groove width islarger than the coil width. The spring force is applied radially.

Grooves for axial springs. (Table 1a, row 5, column 2) Grooves for axialsprings are designed to better retain the spring at assembly. In suchcases, the groove width is smaller than the coil height. At assembly,the spring is compressed along the minor axis axially and upon theinsertion of a pin or shaft through the ID of the spring the spring, thecoils deflect along the minor axis axially.

There are variations of these grooves from a flat bottom groove to atapered bottom groove.

Axial springs using flat bottom groove. In such cases, the degree ofdeflection available on the spring is reduced compared to a radialspring, depending on the interference that occurs between the coilheight and the groove width.

The greater the interference between the spring coil height and thegroove, the higher the force to deflect the coils and the higher theinsertion and running forces.

In such cases, the spring is loaded radially upon passing a pin throughthe ID. The deflection occurs by turning the spring angularly in thedirection of movement of the pin. An excessive amount of radial forcemay cause permanent damage to the spring because the spring coils have“no place to go” and butts.

Axial springs with grooves with a tapered bottom. (Table 1b, rows 7-9,column 2 through Table 1c, rows 2-7, column 2) A tapered bottom groovehas the advantage that the spring deflects gradually compared to a flatbottom groove. When a pin is passed through the ID of the spring, itwill deflect in the direction of motion. The running force depends onthe direction of the pin and the type of spring. Lower forces will occurwhen the pin moves in a concave spring direction (Table 1b, row 5,column 6) and higher force when the pin moves in a convex springdirection (Table 1b, row 5, column 8).

Tapered bottom grooves have the advantage that the spring has asubstantial degree of deflection, which occurs by compressing the springradially, thus allowing for a greater degree of tolerance variationwhile remaining functional as compared to flat bottom grooves.

Mounting of groove. Grooves can be mounted in the piston or in thehousing, depending on the application. Piston mounted grooves aredescribed in Tables 2a-2g.

Expansion and contracting of springs. A radial spring ring can beexpanded from a small inside diameter to a larger inside diameter andcan also be compressed from a larger OD to a smaller OD by crowding theOD of the spring into the same cavity. When expanding a spring the backangle and front angles of the spring coils decrease, thus increasing theconnecting and running forces. When compressing a radial spring OD intoa cavity, which is smaller than the OD of the spring, the coils aredeflected radially, causing the back and front angles to increase. Theincrease of these angles reduces the insertion and running forces whenpassing a pin through the ID of the spring.

The following patents and patent application are to be incorporated inthis patent application as follows:

-   -   1) U.S. Pat. No. 4,893,795 sheet 2 FIGS. 4, 5A, 5B, 5C, 5D, 5E,        6A and 6B;    -   2) U.S. Pat. No. 4,876,781 sheet 2 and sheet 3 FIGS. 5A, 5B, and        FIG. 6.    -   3) U.S. Pat. No. 4,974,821 page 3 FIGS. 8 and 9    -   4) U.S. Pat. No. 5,108,078 sheet 1 FIGS. 1 through 6    -   5) U.S. Pat. No. 5,139,243 page 1 and 2 FIGS. 1A, 1B, 2A, 2B and        also FIG. 4A, 4B, 5A, and 5E    -   6) U.S. Pat. No. 5,139,276 sheet 3 FIGS. 10A, 10B, 10C, 11A,        11B, 12A, 12B, 12C, 13A, 13B, and 14    -   7) U.S. Pat. No. 5,082,390 sheet 2 and 3, FIGS. 4A, 4B, 5A, 5B,        6A, 6B, 7A, 7C, 8A, 8B    -   8) U.S. Pat. No. 5,091,606 sheets 11, 12, and 14. FIGS. 42, 43,        44, 45, 46, 47, 48, 48A, 48B, 49, 50A, 50B, 50C, 51A, 51B, 51C,        58A, 58B,    -   9) U.S. Pat. No. 5,545,842 sheets 1, 2, 3, and 5. FIGS. 1, 4, 6,        9, 13, 14, 19, 26A, 26B, 27A, 27B, 28A, 28B.    -   10) U.S. Pat. No. 5,411,348 sheets 2, 3, 4, 5, and 6. FIGS. 5A,        5C, 6A, 6C, 7A, 7C, 7D, 8A, 8B, 8C, 9A, 9C, 10C, 11, 12 and 17.    -   11) U.S. Pat. No. 5,615,870 Sheets 1-15, Sheets 17-23 with FIGS.        1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18,        19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33, 34,        35, 36, 37, 38, 39, 40, 41, 42, 43, 44, 45, 46, 47, 48, 49, 50,        51, 52, 53, 54, 55, 56, 57, 58, 59, 60, 61, 66, 67, 68, 69, 70,        71, 72, 73, 74, 75, 76, 77, 78, 79, 80, 81, 82, 83, 84, 85, 86,        87, 88, 92, 93, 94, 95, 96, 97, 98, 99, 100, 101, 102, 103, 104,        105, 106, 107, 108, 109, 110, 111, 112, 113, 114, 115, 116, 117,        118, 119, 120, 121, 123, 124, 125, 126, 127, 128, 129, 130, 131,        132, 133, 134, 135.    -   12) U.S. Pat. No. 5,791,638 Sheets 1, 2, 3, 4, 5, 6, 7, 8, 9,        10, 11, 12, 13, 14, 15, 17, 18, 19, 20, 21, 22, 23. FIGS. 1-61        and 66-88 and 92-135.    -   13) U.S. Pat. No. 5,709,371, page 1, 2, 3, 4, 5, 6, 7, 8, 9, 10,        11, 12, 13, 14, 15, 17, 18, 19, 20, 21, 22, 23. FIGS. 1-61 and        66-88 and    -   14) Application for patent by Balsells entitled “Spring Holding        Connectors” Customer Ser. No. 10/777,974 filed Feb. 12, 2004.

In general, Tables 1a-1g illustrate housing mounted designs for holdingand other applications. These tables show 53 different types of groovesand spring geometries in which the spring is mounted in the housing,using different spring configurations and different groove variations,which result in different insertion and running forces.

Table 1a, row 2, columns 2-12 show a flat bottom groove with a radialspring.

Table 1a, row 2, column 2 shows an assembly with a spring mounted in ahousing with a shaft moving forward axially.

Table 1a, row 2, column 3 shows the assembly in a latched position.

Table 1a, row 2, column 4 shows schematic of a flat bottom groove.

Table 1a, row 2, column 5 shows and enlarged portion of Table 1A, row 2,column 2.

Table 1a, row 2, column 6 shows the assembly in a hold running connectdirection

Table 1a, row 2, column 7 shows an enlarged portion of Table 1a, row 2,column 3 in a latch position.

Table 1a, row 2, column 8 shows the assembly in a hold runningdisconnect direction.

Table 1a, row 2, column 9 shows the assembly returning to the insertingposition.

Table 1a, row 2, column 10 shows an enlarged view of the point ofcontact between the coils and the shaft.

Table 1a, row 2, column 11 shows an enlarged view of Table 1a, row 2,column 3.

Table 1a, row 2, column 12 shows a cross section of the radial springwith the dot indicating the front angle.

Table 1a, row 2, column 13 shows the spring in a free position and showsa front view of the canted coil counterclockwise radial spring with thefront angle in front.

Table 1a, row 3, columns 2-12 show a spring mounted 180° from that showsin Table 1a, row 2 in a clockwise position. Table 1a, row 4, columns1-12 show a V-bottom groove with a counterclockwise radial spring.

Table 1a, row 5, columns 1-12 show a flat bottom axial groove with an RFaxial spring. The groove width is smaller than the coil height and thepoint of contact is closer to the centerline of the major axis of thespring coil. The closer the point of contact is to the point at the endof the major axis of the coil, the higher the force required todisconnect in a convex direction. (Table 1a, row 5, columns 7-8).Table 1a, row 6, columns 2-12 show a flat bottom groove with an F axialspring. The groove width is smaller than the coil height.Table 1a, rows 7-8 and Table 1b, row 9 show a radial spring turned intoan axial spring by assembling this spring into a cavity in an axialposition.

More specifically, Table 1a, row 6 shows a flat bottom axial groove withcounterclockwise radial spring mounted in an RF axial position. Thegroove width is smaller than the coil height.

Table 1a, row 8 is a flat bottom groove with a counterclockwise radialspring mounted in an F axial position.

Table 1a, row 9 is a flat bottom groove with a clockwise radial springmounted in an RF axial position. The groove width smaller than the coilheight, and

Table 1b, row 2 shows a flat bottom axial groove with clockwise radialspring mounted in F axial position. Groove width smaller than the coilheight.

Table 1b, row 3 shows a V bottom groove with an RF axial spring. Thegroove width is smaller than the coil height.

Table 1b, row 4 shows a flat bottom groove with an RF axial spring witha groove width larger than the coil height. Making the groove widthlarger than the coil heights allows the point of contact to move furtheraway from the point at the end of the major axis of the coil atdisconnect thus decreasing the force.Table 1b, row 5 shows a V bottom flat groove with RF axial spring. Thegroove width is larger than the coil height. (GW>CH)Table 1b, row 6 shows a design like Table 1b, row 5, except that the RFaxial spring has offset coils that fit into the groove. The offset coilsallow partial contact holding within the groove at different intervalsalong the groove diameter walls, and the coils are deflected axially atdifferent points of the groove on both sides sufficiently to retain thespring in place. The offset coils increase the total axial coil height,which helps retain the spring inside the groove. The insertion andrunning forces are also reduced compared to Table 1b, row 5 where thegroove width is smaller than the coil height. The difference in force isillustrated in Table 1b, row 6, column 12, where force versus shafttravel distance is shown illustrating the force developed.

Table 1b, row 6, column 13 and 14 shows the offset coils in a freeposition.

Table 1b, row 6, column 11 shows the point of contact in relation to thepoint at the end of the major axis of the coils with the point ofcontact further away from the major axis of the coil thus decreasing theforce required to disconnect. This can be compared with Table 1b, row 8,column 11 whereby the point of contact is closer to the point at the endof the major axis of the coil, thus requiring a substantially higherforce to disconnect.

Table 1b, row 7 shows an axial RF spring with a tapered bottom groovethat positions the point of contact (Table 1b, row 7, column 11) closerto the end point at the end of the major axis of the coil than in Table1b, row 6, column 11, thus requiring a greater force to disconnect.Table 1b, row 8 shows a tapered bottom groove of a differentconfiguration but similar to Table 1b, row 7 with an RF axial springwith a groove width smaller than the coil height. The grooveconfiguration positions the point of contact closer to the end point atthe end of the major axis of the coil. An axial RF spring is used inthis design.

Table 1b, row 9 shows a tapered bottom groove with RF axial spring witha groove width smaller than the coil height.

The point of contact is positioned at the end point of the major axis ofthe coil and disconnect is not possible as the force is applied alongthe major axis since the spring will not compress along that axis.

Table 1c, row 2 shows a tapered bottom groove with an axial springmounted in the groove. The position of the spring is such that thecenterline along the minor axis is slightly above the bore, whichresults in less deflection of the spring, thus positioning the point ofcontact further away from the end point of the major axis of the coil,resulting in a lower disconnect force.

Table 1c, row 3 shows a tapered bottom groove with an axial springmounted in the groove. The groove is shown with a 25-degree angle. Byincreasing the angle, the distance from the end of the major axis of thecoil to the point of contact increases (Table 1c, row 3, column 11compared to Table 1b, row 8, column 11), resulting in lower connect anddisconnect forces. On the other hand, decreasing the taper angle willbring the point of contact closer to the end of the major axis of thecoil, resulting in higher connect and disconnect forces. Increasing thegroove angle will increase the spring deflection which will increase therunning force.

Table 1c, row 4 shows a tapered bottom groove with an RF axial springwith the shaft inserted in the opposite direction. The groove width issmaller than the coil height. In this case, again, the point of contactat the point at the end of the major axis of the coil and no deflectionexists and a disconnect is not possible.

Insertion force in this direction will cause the spring coil to turncounter clockwise thus applying a force along the major axis of the coiland the spring will not deflect along the major axis causing damage tothe spring.

Table 1c, row 5 shows a tapered bottom groove with 45° turn angle springwith the shaft inserted in the convex direction. The groove width issmaller than the coil width. The angular spring deflects axially.

Table 1c, row 6 shows a tapered bottom groove with an RF axial springfilled with an elastomer with a hollow center. The groove width issmaller than the coil height (GW<CH).

Table 1c, row 7 Shows a tapered bottom groove with an RF axial springfilled with an elastomer solid, as in Table 1c, row 6 with the groovewidth smaller than the coil height (GW<CH).

Table 1c, row 8 shows a step round flat bottom groove with an RF axialspring groove with the width smaller than the coil height. This designhas a groove with a point of contact that scrapes the wire as the coilmoves, removing oxides that may be formed on the surface of the wire.The groove has been designed to provide a lower force at disconnect byincreasing the distance between the point of contact and the point atthe end of the major axis of the coil.Table 1c, row 9 shows an inverted V bottom groove with RF axial spring.The groove width is smaller than the coil height.Table 1d, row 2 shows a tapered bottom groove with a counterclockwiseradial spring mounted in a RF position. The groove width is smaller thanthe coil height. Notice the position of the point of contact withrespect to the end point at the end of the major axis of the coil. Thecloser the point of contact to the end point at the end of the majoraxis of the coil the higher the force required to disconnect.Table 1d, row 3 shows a tapered bottom groove with a counterclockwiseradial spring mounted in an F axial position. The groove width issmaller than the coil height.Table 1d, row 4 shows a tapered bottom groove with a clockwise radialspring mounted in an RF axial position. The groove width is smaller thanthe coil height.Table 1d, row 5 shows a tapered bottom groove with a clockwise radialspring mounted in an F axial position. The groove width is smaller thanthe coil height.Table 1d, row 6 shows a dovetail groove with a counterclockwise radialspring.Table 1d, row 7 shows a special groove with a counterclockwise radialspring.Table 1d, row 8 shows an angle of zero to 22½ degrees flat and taperedbottom groove with a counterclockwise radial spring. The groove width isgreater than the coil width. The spring in latching will turn clockwisepositioning the coil to reduce the force required to disconnect bypositioning the point of contact further away from the end of the endpoint at the end of the major axis of the coil.Table 1d, row 9 shows an angle of 0 to 22½ degrees. The piston groovehas a flat and a tapered bottom with a clockwise spring. The spring hasan ID to coil height ratio smaller than 4. Under load, this spring has ahigher torsional force that requires a higher force to connect ordisconnect the shaft. Upon latching, the spring turns clockwise, movingthe point of contact closer to the end of the major axis of the coil(Table 1d, row 9, column 7 and Table 1d, row 9, column 11) thusincreasing the force to disconnect.Table 1e, row 2 is like Table 1d, row 9 except that in this case, thespring groove has an ID to coil height ratio greater than 4, thus theradial force applied to the spring at connect or disconnect issubstantially lower. As the ratio of the ID of the spring to the coilheight increases, the force required to connect or disconnect decreasesdue to a lower radial force.Table 1e, row 3 has an angle groove with a 0° to 22.5° piston grooveangle similar to FIG. 3 except that the piston groove has a ‘V’ bottomgroove instead of a ‘V’ bottom groove with a flat. The housing has a ‘V’bottom groove with a flat at the bottom of the groove. This designpermits for specific load points at connect-latched position.Table 1e, row 4 shows a groove angle 30°/22½° bottom groove with acounterclockwise radial spring. The groove width is greater than thecoil width. By changing the groove angle, the distance between the pointof contact and the point at the end of the major axis of the coil isincreased, reducing the force at disconnect.Table 1e, row 5 shows an angle 60°/22½° bottom groove with acounterclockwise radial spring. The groove width is greater than thecoil width.Table 1e, row 6 shows a special V type bottom with a 23° and 60° anglewith a counterclockwise radial spring. The groove width greater than thecoil width.Table 1e, row 7 shows a V type bottom groove with 23° and 60° angleslike Table 1e, row 6 with a counterclockwise radial spring. The groovewidth is greater than the coil width. By moving the shaft forward andthen back it causes the spring to turn so the point of contact is closerto the point at the end of the major axis of the coil, increasing theforce required to disconnect. When the direction of latching isreversed, the piston is traveling in the direction of the back angle inTable 1e, row 8, column 2, as opposed to traveling in the direction ofthe front angle in Table 1e, row 7, column 2. The increased forceincreases the turning of the spring, thus increasing the distancebetween the point of contact and the end point of the major axis,decreasing the force required to disconnect or unlatch. Compare Table1e, row 7, column 8 showing the piston moving forward and the positionof the point of contact “A” with the position of the point of contactTable 1e, row 7, column 7.Table 1e, row 9 shows a special V bottom type groove with 22° and 60°angles with a radial spring The contact point is close to the point atthe end of the major axis of the coil for a high disconnect force.Table 1e, row 10 through Table 1f, row 5 show turn angle springs,assembled in different groove designs. Notice the point of contactposition in relation to the POINT AT THE END OF THE major axis of thecoil.

More specifically, Table 1e, row 10 shows a special V-bottom with 23°and 60° angles with a 20° turn angle spring.

Table 1f, row 2 shows a special V-bottom with 30° and 60° angles with a20° turn angle spring.

Table 1f, row 3 shows a special V-bottom with 60° and 49° angles with a20° turn angle spring.

Table 1f, row 4 shows a special groove with a 45° turn angle spring. Inthis case, the point of contact is closer to the point at the end of theminor axis of the coil. Upon insertion, the pin will cause the spring toexpand radially and causing the coil to deflect along the minor axis andcausing the spring coils to turn counterclockwise to connect. Atdisconnect the spring coils will deflect along the minor axis and thecoils will continue to turn counterclockwise to disconnect. The springcoils will turn clockwise to its original position when the force actingon the spring is released.Table 1f, row 5 shows a special tapered groove with a 30° angle with a45° angle at the piston groove. Notice the point of contact in relationto the point at the end of the major axis of the coil.Table 1f, rows 6-8 show an axial spring mounted in a tapered bottomgroove.

More specifically, Table 1f, row 6 shows an angular groove with an RFaxial spring with a groove depth greater than the coil width. Notice theposition of the point of contact at disconnect with the coil diameterexpands radially permitting disconnect.

Table 1f, row 7 shows a groove similar to FIG. 3 a, but with a taperedangle on one side of the groove.

Table 1f, row 8 shows a symmetrical angle groove with an RF axialspring. The groove depth is greater than the coil width.

Table 1f, row 9 shows a flat bottom-housing groove with acounterclockwise radial spring. The groove width is greater than thecoil height. In this case, the piston has a step groove.

Table 1g, rows 2-6 show various methods of mounting a panel on ahousing, using a length of spring whose groove can be mounted on thehousing or on the panel and such groove has a groove width smaller thanthe coil height so that the spring can be retained in such groove.Table 1g, row 2 shows a panel-mounted design with length of spring withaxial loading and holding.Table 1g, row 2, column 2 shows the panel in an inserting position.Table 1g, row 2, column 3 shows the panel in a connected position. Table1g, row 2, column 4 shows a schematic of the groove design. Table 1g,row 2, column 5 shows the spring being inserted into the cavity. Table1g, row 2, column 7 shows the spring in a holding position. Table 1g,row 2, column 11 shows an enlarged view of Table 1g, row 2, column 7.Table 1g, row 3 shows a panel mounting design with length of spring withsome axial loading and latching, using a flat tapered groove. The groovewidth is smaller than the coil height. This particular design willpermit axial movement of the panel. Table 1g, row 2, column 3 shows thedesign in a latch position, which can permit axial movement. Table 1g,row 3, column 8 shows an enlarged view of the latch position. Table 1g,row 3, column 5 shows the point in contact in relation to the end majoraxis of the coil.Table 1g, row 4 shows a panel mounting design with length of spring withlatching, which will permit axial movement of the panel and locking,using a rectangular groove on the panel with the groove width smallerthan the coil height.Table 1g, row 4, column 3 shows the design in a latch axial position,permitting some axial movement. Table 1g, row 4, column 5 shows anenlarged view of the latch position. Table 1g, row 4, column 9 shows alatch locked position to disconnect. Table 1g, row 4, column 11 shows anenlarged view of the point of contact with end of major axis of the coilat locking.Table 1g, row 5 shows a panel mounting with length of spring with axialloading and latching. Groove width smaller than the coil height.Table 1g, row 5, column 2 shows the panel in an inserting position andTable 1g, row 5, column 3 in a latched position with the spring retainedin the groove mounted in the housing with the grooves offset from eachother. The grooves are offset to provide axial loading in the latchedposition. In this case, the panel has a V-groove design. Notice theaxially loaded position of the spring to prevent axial movement when ina connected-latched position.Table 1g, row 6 shows a panel assembly similar to Table 1g, row 5 exceptthat the panel has a step flat bottom groove instead of a V-bottom typegroove and the housing has a flat tapered bottom groove and it isaxially loaded in the connect position. Disconnect in the axial positionwill not be possible because as the panel is pulled it causes the springto turn, applying the disconnect component force at the end of the majoraxis of the coil where no deflection occurs.The descriptions illustrated in Tables 1g, rows 2-6 show the holding,latching, and locking in the axial position. Separation of the panelfrom the housing can be done by sliding the panel longitudinally.These designs indicated in Table 1g, rows 2-6 show a panel-mounteddesign; however, the design could also be applicable to other designs,such as cylindrical, rectangular, elliptical or other types of surfaces.All designs are shown with GW<CH; however the groove could be made widerto be GW<CH with lower connect-disconnect force.Table 1g, rows 7-9 are similar to Table 1e, row 3, show differentmethods of retaining the spring in the cavity.Table 1g, row 7 shows a rectangular washer retaining the spring inposition.Table 1g, row 8 shows a snap ring retaining the spring in position.Table 1g, row 9 shows a washer retained in position by rolling over aportion of the housing on to the washer housing to form the retaininggroove.The designs are shown with specific dimensions, angles and grooveconfigurations. These values can be changed to other angles and grooveconfigurations while achieving the results indicated.Piston Mounted Designs for Latching Applications.

Table 2a-2g show various designs with the spring mounted in the pistonin latching applications. In essence, these applications are similar tothe ones that are described in Tables 1a-1g except that the spring ismounted in the piston and it encompasses 48 variations of groovedesigns.

Table 2a, row 2 shows a flat bottom groove with counterclockwise radialspring with a groove width greater than the coil width. Table 2a,columns 2-9, show different assemblies of the spring and grooves and thespring in various positions.

Table 2a, row 2, column 2 shows the assembly in an insert position.

Table 2a, row 2, column 3 shows the assembly in a latch position.

Table 2a, row 2, column 4 shows the cross section of the flat bottomgroove.

Table 2a, row 2, column 5 shows an enlarged view of Table 2a, row 2,column 2.

Table 2a, row 2, column 6 shows the position of the spring in ahold-RUNNING position with the spring deflected along the minor axis.

Table 2a, row 2, column 7 shows an enlarged position of Table 2a, row 2,column 3 in a latched-connect position moving in a disconnect directionrelative to the end point of the major axis.

Table 2a, row 2, column 8 shows the assembly in hold-disconnectdirection.

Table 2a, row 2, column 9 shows the assembly returning to the insertingposition.

Table 2a, row 2, column 10 shows the spring in a free position.

Table 2a, row 2, column 11 shows a partial enlarged view of Table 2a,row 2, column 7.

Table 2a, row 2, column 12 shows a cross sectional view of the springshowing the position of the front angle.

Table 2a, row 2, column 13 shows a front view of the spring in acounterclockwise with the radial spring front angle in the front.

Table 2a, row 3, is the same position as Table 2a, row 2 except that thespring has been turned around 180°.

Table 2a, row 4 shows a V-bottom groove with a counterclockwise radialspring with a groove width greater than the coil width.

Table 2a, row 5 shows a flat bottom axial groove with an RF axialspring. The groove width is smaller than the coil height. The point ofcontact is close to the end point of the major axis of the coil,requiring a high force to disconnect.

Table 2a, row 6 shows a design as in Table 2a, row 5 except it uses an Fspring.

Table 2a, rows 7-9 and Table 2b, row 2 shows a radial spring turned intoan axial spring, using a flat bottom groove.

Table 2b, row 3 shows a V-bottom groove with an RF axial spring. Thegroove width is smaller than the coil height.

Table 2b, row 4 shows a flat bottom groove with an RF axial spring. Thegroove width is greater than the coil height, thus resulting in lowerdisconnect force.

Table 2b, row 5 shows a V-bottom tapered groove with an RF axial spring.The groove width is greater than the coil height.

Table 2b, row 6 shows a design like Table 2b, row 8, except that the RFaxial spring has offset coils that fit into the groove. The offset coilsallow partial contact holding within the groove at different intervalsalong the groove diameter walls, and the coils are deflected axially atdifferent points of the groove on both sides sufficiently to retain thespring in place. The offset coils increase the total axial coil height,which helps retain the spring inside the groove. The insertion andrunning forces are also reduced compared to Table 2b, row 8 where thegroove width is smaller than the coil height. The difference in force isillustrated in Table 2b, row 5, column 12, where we show force versusshaft travel distance, illustrating the force developed in Table 2b, row7 and in Table 2b, row 6.Table 2b, row 6, column 12 shows a diagram Force vs. Shaft TravelDistance that compares the force developed by Table 2b, row 7 vs. Table2b, row 6.Table 2b, row 6, columns 14-15 shows the offset coils in a freeposition.Table 2b, row 6, column 11 shows the point of contact in relation to thepoint at the end of the major axis of the coils with the point ofcontact further away from the end point of the major axis of the coilthus decreasing the force required to disconnect. This can be comparedwith Table 2b, row 7, column 11 whereby the point of contact is closerto the end point of the major axis of the coil, thus requiring asubstantially higher force to disconnect.Table 2b, row 7 shows an axial RF spring with a tapered bottom groovethat positions the point of contact (Table 2b, row 7, column 11) closerto the end point of the major axis of the coil than in Table 2b, row 6,column 11, thus requiring a greater force to disconnect.Table 2b, row 8 shows a tapered bottom groove of a differentconfiguration but similar to Table 2b, row 7 with an RF axial springwith a groove width smaller than the coil height. The grooveconfiguration positions the point of contact closer to the end point atthe end of the major axis of the coil. An axial RF spring is used inthis design.

Table 2b, row 9 shows a tapered bottom groove with RF axial spring witha groove width smaller than the coil height. The end point of contact ispositioned at the point of contact at the end point of the major axis ofthe coil and disconnect is not possible as the force is applied alongthe major axis since the spring will not compress along that axis.

Table 2c, row 2 shows a tapered bottom groove with an axial springmounted in the groove. The position of the spring is such that thecenterline along the minor axis is slightly above the bore, thuspositioning the point of contact further away from the end point of themajor axis of the coil, resulting in a lower disconnect force.

Table 2c, row 3 shows a tapered bottom groove with an axial springmounted in the groove. The groove is shown with a 25-degree angle. Byincreasing the angle, the distance from the end point of the major axisof the coil to the point of contact increases (Table 2c, row 3, column11 compared to Table 2b, row 9, column 11), resulting in lower connectand disconnect forces. On the other hand, decreasing the taper anglewill bring the point of contact closer to the end point of the majoraxis of the coil, resulting in higher connect and disconnect forces.Increasing the groove angle will increase the spring deflection whichwill increase the running force (Table 1c, row 2, column 6, Table 1c,row 3, column 8).

Table 2c, row 4 shows a tapered bottom groove with an RF axial springwith the shaft inserted in the opposite direction. The groove width issmaller than the coil height. In this case, again, the point of contactis at the end point of the major axis of the coil and no deflectionexists and a disconnect is not possible.Table 2c, row 5 shows a tapered bottom groove with 45° turn angle springwith the shaft inserted in the convex direction. The groove width issmaller than the coil width. The angular spring deflects axially.Table 2c, row 6 shows a tapered bottom groove with an RF axial springfilled with an elastomer with a hollow center. The groove width issmaller than the coil height (GW<CH).Table 2c, row 7 shows a tapered bottom groove with an RF axial springfilled with an elastomer solid, as in Table 2c, row 6 with the groovewidth smaller than the coil height (GW<CH).Table 2c, row 8 shows a step round flat bottom groove with an RF axialspring groove with the width smaller than the coil height. This designhas a groove with a point of contact that scrapes the wire as the coilmoves, removing oxides that may be formed on the surface of the wire.The groove has been designed to provide a lower force at disconnect byincreasing the distance between the point of contact and the end pointof the major axis of the coil.Table 2c, row 9 shows an inverted V bottom groove with an RF axialspring. The groove width is smaller than the coil height.Table 2d, row 2 shows a tapered bottom groove with a counterclockwiseradial spring mounted in an RF position. The groove width is smallerthan the coil height. Notice the position of the point of contact withrespect to the end point at the end of the major axis of the coil. Thecloser the point of contact to the end point of the major axis of thecoil, the higher the force required to disconnect.Table 2d, row 3 shows a tapered bottom groove with a counterclockwiseradial spring mounted in an F axial position. The groove width issmaller than the coil height.Table 2d, row 4 shows a tapered bottom groove with a clockwise radialspring mounted in an RF axial position. The groove width is smaller thanthe coil height.Table 2d, row 5 shows a tapered bottom groove with a clockwise radialspring mounted in an F axial position. The groove width is smaller thanthe coil height.Table 2d, row 6 shows a dovetail groove with a counterclockwise radialspring.Table 2d, row 7 shows a special groove with a counterclockwise radialspring.Table 2d, row 8 shows an angle of zero to 22½ degrees flat and taperedbottom groove with a counterclockwise radial spring. The groove width isgreater than the coil width. The spring in latching will turn clockwisepositioning the coil to reduce the force required to disconnect bypositioning the point of contact further away from the end of the endpoint at the end of the major axis of the coil.Table 2d, row 9 shows an angle of 0 to 22½ degrees. The piston groovehas a flat and a tapered bottom with a clockwise spring. The spring hasan ID to coil height ratio smaller than 4. Under load, this spring has ahigher torsional force that requires a higher force to connect ordisconnect the shaft. Upon latching, the spring turns clockwise, movingthe point of contact closer to the end point of the major axis of thecoil (Table 2d, row 9 column 7, column 11) thus increasing the force todisconnect.Table 2e, row 2 is like Table 2d, row 9 except that in this case, thespring groove has an ID to coil height ratio greater than 4, thus thetorsional force applied to the spring at connect or disconnect issubstantially lower. As the ratio of the ID of the spring to the coilheight increases, the force required to connect or disconnect decreasesdue to a lower torsional force.Table 2e, row 3 has an angle groove with a 0° to 22.5° piston grooveangle similar to Table 2a, row 4 except that the piston groove in Table2e, row 3 has a ‘V’ bottom groove instead of a ‘V’ bottom groove with aflat. The housing in Table 2e, row 3 has a ‘V’ bottom groove with a flatat the bottom of the groove. This design permits for specific loadpoints at connect-latched position.Table 2e, row 4 shows a groove angle 30°/22½° bottom groove with acounterclockwise radial spring. The groove width is greater than thecoil width. By changing the groove angle, the distance between the pointof contact and the end point of the major axis of the coil is increased,reducing the force at disconnect.Table 2e, row 5 shows an angle 60°/22½° bottom groove with acounterclockwise radial spring. The groove width is greater than thecoil width.Table 2e, row 6 shows a special V type bottom with a 23° and 60° anglewith a counterclockwise radial spring. The groove width is greater thanthe coil width.Table 2e, rows 7-8 show a V type bottom groove with 23° and 60° angleslike Table 2e, row 6 with a counterclockwise radial spring. The groovewidth is greater than the coil width. By moving the shaft forward andthen back we cause the spring to turn so the point of contact is closerto the end point at the end of the major axis of the coil, increasingthe force required to disconnect. When the direction of latching isreversed, the piston is traveling in the direction of the back angle inTable 1e, row 7, as opposed to traveling in the direction of the frontangle in Table 1e, row 6. The increased force increases the turning ofthe spring, thus increasing the distance between the point of contactand the end point of the major axis, increasing the force required todisconnect or unlatch. Compare Table 2e, row 7, column 8 showing thepiston moving forward and the position of the point of contact “A” withthe position of the point of contact Table 2e, row 8, column 7.Table 2e, row 9 shows a special V bottom type groove with 22° and 60°angles with a radial spring. The contact point is close to the end pointat the end of the major axis of the coil for a higher disconnect force.Table 1f, rows 2-6 show turn angle springs, assembled in differentgroove designs. Notice the point of contact position in relation to theend point of the major axis of the coil.Table 2f, row 2 shows a special V-bottom with 23° and 60° angles with a20° turn angle spring.Table 2f, row 3 shows a special V-bottom with 30° and 60° angles with a20° turn angle spring.Table 2f, row 4 shows a special V-bottom with 30° and 49° angles with a20° turn angle spring.Table 2f, row 5 shows a special groove with a 45° turn angle spring. Inthis case, the point of contact is closer to the end point at the end ofthe minor axis of the coil. Upon insertion, the pin will cause thespring to contract radially (Table 2f, row 5, column 2) and causing thecoil to deflect along the minor axis (Table 2f, row 5, column 6) andcausing the spring coils to turn counterclockwise to connect (Table 2f,row 5, column 7). At disconnect the spring coils will deflect along theminor axis and the coils will continue to turn counterclockwise todisconnect (Table 2f, row 5, column 8). The spring coils will turnclockwise to its original position (Table 2f, row 5, column 9) when theforce acting on the spring is released.Table 2f, row 6 shows a special tapered groove with a 30° angle with a45° angle at the piston groove. Notice the point of contact in relationto the end point at the end of the major axis of the coil.Table 2f, row 7 shows a flat bottom-housing groove with acounterclockwise radial spring. The groove width is greater than thecoil height. In this case, the piston has a step groove.Table 2f, row 8 shows a panel mounted design with length of spring withaxial loading and holding.Table 2f, row 8, column 2 shows the panel in an insert position. Table2f, row 8, column 3 shows the panel in a connected position. Table 2f,row 8, column 4 shows a schematic of the groove design. Table 2f, row 8,column 5 shows the spring being inserted into the cavity. Table 2f, row5, column 7 shows the spring in a holding position. Table 2f, row 8,column 11 shows an enlarged view of Table 2f, row 5, column 7 with thepanel bottoming.Table 2f, row 9 shows a panel mounting design with length of spring withsome axial loading and latching, using a flat tapered groove. The groovewidth is smaller than the coil height. This particular design willpermit axial movement of the panel. Table 2f, row 9, column 3 shows thedesign in a latch position, which will permit axial movement. Table 2f,row 9, column 7 shows an enlarged view of the latch position.Table 2f, row 9, column 11 shows the point in contact in relation to theend point of the major axis of the coil.Table 2g, row 2 shows a panel mounting design with length of spring thatwill permit axial movement of the panel and locking, using a rectangulargroove on the housing with the groove width smaller than the coilheight.Table 2g, row 2, column 3 shows the design in a latch axial position,permitting some axial movement. Table 2g, row 2, column 7 shows anenlarged view of the latch locking means and Table 2g, row 5, column 10shows an enlarged view of the point of contact with end of major axis ofthe coil.Table 2g, row 3 shows a panel mounted design using a length of spring.The groove width is smaller than the coil height. Table 2g, row 3,column 2 shows the panel in an inserting position and Table 2g, row 3,column 3 in a latched position with the spring retained in the groovemounted in the housing with the grooves offset from each other. Thegrooves are offset to provide axial loading in the latched position. Inthis case, the panel has a V-groove design. Notice the axially loadedposition of the spring to prevent axial movement when in aconnected-latched position.Table 2g, row 4 shows a panel assembly similar to Table 2g, row 3 exceptthat the panel has a step flat bottom groove instead of a V-bottom typegroove and the panel has a flat tapered bottom groove and it is axiallyloaded in the connect position. Disconnect in the axial position willnot be possible because as the panel is pulled it causes the spring toturn, applying the disconnect component force at the end point of themajor axis of the coil where no deflection occurs. The descriptionsillustrated in Table 2f, row 8 through Table 2g, row 4 show the holding,latching, and locking in the axial position. Separation of the panelfrom the housing can be done by sliding the panel longitudinally.The designs indicated in Table 2f, row 8 through Table 2g, row 4 show apanel mounted design; however the design could also be applicable toother designs, such as cylindrical, rectangular, elliptical or othertypes of surfaces. All designs are shown with GW<CH; however the groovecould be made wider to be GW<CH with lower connect-disconnect force.The designs are shown with specific dimensions, angles and grooveconfigurations. These values can be changed to other angles and grooveconfigurations while achieving the results indicated.Spring Characteristics that Affect PerformanceSpring design and installation factorsUsing an axial spring to enhance retention of the spring in the grooveor using a radial spring turned into an axial spring at installation.Using an axial spring or a radial spring turned into an axial spring atinstallation to increase initial insertion, running and disconnectforcesChanging the coil width to coil height ratioWhen the coil width to height ratio is close to one, the spring willturn easier reducing forces since the spring is round.The smaller the coil width to coil height ratio, the smaller the backangle. The smaller the back angle, the higher the insertion forcerequired when the piston is inserted in the spring into the back anglefirst. The opposite is true when the coil width to coil height ratio isreversed, i.e., the back angle is larger and the insertion forces arelower.Using an F axial spring to increase the insertion running and disconnectforces compared to an RF spring.Using an RF axial spring to reduce the insertion, running, anddisconnect forces.Using an offset axial spring to reduce the initial insertion runningforce, and disconnect forces.Using a Length of Spring Mounted in an Axial Type Groove for PanelApplicationsUsing a spring with a ratio of ID to coil height to vary insertion,connect and the disconnect forces. As the ratio increases, the forceswill decrease or vice versa as the ratio decreases the forces increase.Using springs with varying turn angles to vary forces.Using an axial spring with offset coils where the groove width issmaller than the coil height and addition of the coil height of thevarious coils to reduce insertion, running, connect, and disconnectforces and the ratio of connect to disconnect force.The connect/disconnect forces decrease as the ratio of ID to coil heightincreases.Using variable means to form the ring, ranging from threading the ends,latching the ends, interfacing the ends and butting as opposed towelding.Varying the Device Geometry to Control the ForcesDesigning the groove geometry to position the point of contact atdisconnect relative to the end point of the major axis of the coil.Positioning the end point of the spring major axis. The shorter thedistance to the contact point, the higher the force required todisconnect.Positioning the end point of the spring minor axis. The shorter thedistance to the contact point, the lower the force required todisconnect.Varying the groove design and insertion direction to vary the force.Varying the groove geometry so that the spring torsional force in thelatched position is in an axial direction thus increasing the forcerequired to disconnect and minimizing axial play.Position the latching grooves so that they are offset, causing the axialor radial spring coils to turn, introducing an axial force that reducesaxial play and increases the force required to connect-disconnect. Table1g, row 5, column 12; row 2, Table 2a, row 6, column 6 and row 8, column6.Position the geometry of the latching grooves that will cause the axialand radial spring coils to turn, increasing the force required toconnect-disconnect. FIGS. 12 e and 13 e.The use of multiple springs and grooves to increase the forces and thecurrent carrying capacity.The forces vary according to the direction of the piston insertion.Using threaded grooves with a spring length retained in the groove witha groove width smaller than the coil height.

In accordance with the present invention to attain the maximumdisconnect force, the point of contact should be as close as possible tothe end of the major axis of the coil. Table 1 and Table 2a (rows 5,columns 7 and 11).

To attain the minimum disconnect force, the contact point, should be asclose as possible to the end of the minor axis of the coil. Table 1a andTable 2a (row 1, column 7 and 11).

An axial spring with offset coils mounted in a housing with the groovewidth smaller than the addition of the coil height of the various coils,providing the following features:

Lower spring retention force.

Lower insertion force

Lower ratio of disconnect to connect

Lower ratio of disconnect to running force.

Reference Table 1b and Table 2b, row 6 vs. row 8.

Modification of the groove cavity that affects the position of the pointof contact in relation to the end point of the major axis of the coilthat affects the force required to disconnect, connect. Reference Table1b and Table 2b, row 8 vs. row 9 and row 8, column 4 vs. row 9, column4.Modification of the groove cavity that affects the position of the pointof contact in relation to the end of the major axis of the coil thataffects the force required to disconnect-connect. Reference Table 1b andTable 2b, row 9 vs. Table 1c, 2c, row 2 and Table 1a, 2a, row 9, column4 vs. Table 2a, 2c, row 2, column 4.

The greater the interference between the coil height and the groovewidth, the higher the force required to disconnect. Table 1a and Table2a (row 5, column 5 versus Table 1b, 2b, row 4, column 5) Table 1a, 2a,row 5, column 5 has interference between the coil height and the groovewidth while row 6 shows a clearance between the coil height and thegroove width.

The higher the position of the coil centerline along the minor axis inrelation to the groove depth. (Reference Table 1b and Table 2b, row 8,column 4 versus Table 1c, 2c, row 2, column 4) the higher the forcerequired to disconnect.

The type of axial spring mounted in a housing or piston RF vs. F with RFhaving substantially more deflection but lower force compared to F.Reference Table 1a and Table 2a, row 5, column 2, column 5, and column 6versus row 6, column 2, column 5 and column 6.

Manner and type of spring used affects the force required toconnect/disconnect, using an axial RF or an F spring assembled into agroove whose groove width is smaller than the coil height versus aradial spring turned into an axial spring RF or F spring with coilscanting clockwise or counterclockwise. Reference Table 1a and Table 2a,rows 5 and 6 versus rows 7, 8, 9 and Table 1b, 2b row 2 and also row 8vs. Table 1d, 2d, rows 2-5.

Direction of movement of the piston or housing a radial spring thataffects the force required to connect and disconnect. Reference Tables1d, 2d, row 8, columns 2, 5, 7 and 11 vs. row 9, column 2, 5, 7, and 11due to variation that exists between row 8 and row 9 between the pointof contact and the point at the end of the major axis of the coil thatresults in substantial variation in forces.

The greater the insertion force of an axial spring into a groove whoseGW<CH, the higher the force required to disconnect (Reference Table 1b,2b, row 8, column 5 vs. row 9, column 5).

Radial springs with different ratios of spring ID to coil height mountedin a housing or piston. Reference Table 1d, 2d, row 9 vs. Table 1e, 2e,row 2. The greater the ratio the lower the forces.

Variations of groove configuration affecting the connect-disconnectforce by varying the groove angle. Reference Table 1e, row 3, column 5,column 7, column 11 vs. row 4, column 5, column 7, column 11. Such anglevariation affects the distance between the point of contact and thepoint at the end of the major axis of the coil. The closer these twopoints the higher the force required to disconnect.

The effect of axially loading in the latched position or disconnect andthe effect on initial disconnect force and travel.

A radial spring axially loaded in the latched position will require ahigher initial disconnect force than a non-axially loaded spring.

An axially loaded axial spring will develop a higher initial force asshown in Table 1g, row 2, column 3, column 7, column 11 at disconnectthan a non-axially loaded, and also Table 2f, row 8, column 3, column 7and column 11.

Direction of the spring upon insertion as pointed out by the directionof the arrows. (Canted coil springs always deflect along the minor axisof the coil). The spring turns in the direction of the arrow, as shownin the following:

FIG. 1 a, 1 b forward in the direction of the arrow, Table 1a and Table2a, row 2, column 8 and column 11 in the opposite direction.

An axial spring axially loaded in the latched position will require ahigher disconnect force than a non-axially loaded spring.

Recognizing the direction in which the spring will deflect and may turn,assists in selecting the groove configuration. When the load is applied,the spring always deflects along the minor axis of the coil as it is theeasiest way to deflect. The spring turns when the ratio of the coilwidth to the coil height is equal to 1 or greater. As the ratioincreases, the ability of the spring coils to turn decreases, causingthe spring to deflect instead of turn. Specifically,

A spring with different turn angles in conjunction with differentgrooves to vary the force to connect and disconnect. Turn angles permitthe design of the grooves so that the spring does not have to be turnedat assembly. Reference Table 1f and Table 2f, rows 2, columns 2, 7, 11and row 6, columns 2, 5, 7 11;

Disconnect by expanding the ID of the spring and compressing the coilsalong the minor axis of the coils to affect insertion, connect anddisconnect. Table 1f, rows 6-8;

Housing mounted grooves using a single groove versus a split groove.Note: all drawings in Table 1a show a split groove and Table 2a shows asingle groove in row 4, column 2;

Panel mounted spring with groove width smaller than the coil heightusing a spring in length. Axial latching and axial loading the spring toprevent axial movement. Table 1g, rows 2-3, Table 2g, rows 8-9;

Axial loading the spring coils by offsetting the position of the groovesaxially between the housing and shaft so as to create an axial load onthe spring to reduce or eliminate movement between the shaft andhousing. This configuration has a higher force as shown in FIGS. 4-5;

Multiple springs mounted in multiple single grooves of any of thedesigns in Tables 1a-1g, Tables 2a-2g and in FIGS. 1-18 f with eitherradial or axial springs that can be mounted radially or axially withsprings for variable force retention, play or no play and conductivity.See FIGS. 8 and 9.

Threaded grooves using a spring length retained in the groove having agroove width smaller than the coil height. FIGS. 10 a, 10 b and 10 d;

Threaded grooves using a radial or turn angle spring in length using agroove having a groove width greater than the coil width (GW>CW) Table1a, row 1, column 2, row 4, column 2 and Table 1d, rows 6-9 throughTable 1f, row 5 and Table 2g, row 2 and Table 2f, row 7 and FIGS. 5, 6,7 and 8;

Panel mounted in a housing radial or axial spring in length and thespring can be retained in the panel or the housing for axial holding,latching or locking the panel to the housing and when in a latched orlocked position the panel may be axially loaded to eliminate axial play;

Various types of spring-ring groove mounted designs with variable meansto form a ring, ranging from threading the ends, latching the ends,interfacing the ends and butting, using non-welded springs to form aring. FIGS. 15, 16, 17, and 18;

Different groove configurations that affect the force parameters,depending on the position of the point load in reference to the endpoint of the major axis of the coil that affects the ratio of disconnectto insertion, disconnect to running force, and the disconnect forceswith a radial spring;

A radial or axial spring whose coil width to coil height ratio is onethat will require higher force at connect and disconnect due to thesmaller back angle of the coil. The closer the ratio to one the higherthe force required to disconnect-connect;

The smaller the groove width to coil height ratio, the higher forces.Reference Table 1, row 8, column 4 vs. Table 1, row 9, column 4;

Variation of the groove geometry by including a step groove design tocontrol the position of the contact point relative to the end point ofthe centerline. Table 1f, row 9, column 2, 7, and 11;

Variation of the groove geometry to control the position of the point ofcontact and the end point of the centerline. Table 1f, rows 6-8;

Device with high forces created by offsetting the centerlines of thegrooves as shown in Table 2a, rows 6 and 8;

Reversing the direction of travel in a clockwise or counterclockwiseradial spring will switch from the front angle to the back angle or viceversa, thus changing the relative position of the contact point withrespect to the end point of the centerline thus varying the forces. SeeTable 1e and Table 2e, rows 7, column 8 and row 8, column 7 comparingthe position of the contact point to the end point centerline; and

Retention of radial spring with a dovetail type groove Table 1d and 2d,rows 6-7.

Although there has been hereinabove described a specific spring latchingconnectors radially and axially mounted in accordance with the presentinvention for the purpose of illustrating the manner in which theinvention may be used to advantage, it should be appreciated that theinvention is not limited thereto. That is, the present invention maysuitably comprise, consist of, or consist essentially of the recitedelements. Further, the invention illustratively disclosed hereinsuitably may be practiced in the absence of any element which is notspecifically disclosed herein. Accordingly, any and all modifications,variations or equivalent arrangements which may occur to those skilledin the art, should be considered to be within the scope of the presentinvention as defined in the appended claims.

1. A spring latching connector comprising: a housing having a boretherethrough; a piston slidably received in said bore; a groove formedin one of said bore and piston; a coil spring disposed in said groovefor latching said piston and housing together, said groove being sizedand shaped for controlling, in combination with a spring configuration,disconnect and connect forces of said spring latching connector, saidcoil spring having coils with a major and a minor axis; and a cavityformed in said groove for positioning a point of coil/groove contact inrelation to an end point of the coil major axis in order to determinethe disconnect and connect forces between the spring and the housing. 2.The connector according to claim 1 wherein said groove and coil springare circular.
 3. The connector according to claim 1 wherein the groovecavity positions the point of contact proximate the coil major axis inorder to maximize the disconnect force.
 4. The connector according toclaim 1 wherein the groove cavity positions the point of contactproximate to the end point of the minor axis in order to minimize thedisconnect force.
 5. The connector according to claim 1 wherein a coilheight and a groove width are adjusted to control the disconnect andconnect forces.
 6. The connector according to claim 1 wherein a positionbetween a coil centerline along the minor axis in relation to a groovedepth is adjusted to control disconnect and connect forces.
 7. Theconnector according to claim 1 wherein said spring is turnable in saidgroove for enhancing electrical conduction between said piston and saidhousing by removing oxidation on said spring.
 8. The connector accordingto claim 6 wherein said groove includes an uneven bottom for scrapingsaid spring as said spring turns therepast.
 9. The connector accordingto claim 1 wherein said spring is a counterclockwise radial spring. 10.The connector according to claim 1 wherein said spring is a clockwiseradial spring.
 11. The connector according to claim 1 wherein saidspring is an axial spring having a back angle at an inside diameter ofspring coils and a front angle on an outside diameter of the springcoils.
 12. The connector according to claim 1 wherein said spring is anaxial spring having a back angle on an outside diameter of spring coilsand a front angle on an inside diameter of the spring coils.
 13. Theconnector according to claim 1 wherein said spring is an axial springand the groove has a width smaller than a coil height in order toincrease both spring retention force and increase insertion force. 14.The connector according to claim 13 wherein the axial spring has offsetcoils in order to decrease insertion force.
 15. The connector accordingto claim 1 wherein said groove has a tapered bottom.
 16. The connectoraccording to claim 13 wherein said spring is axial spring having a backangle at an inside diameter of spring coils and a front angle on anoutside diameter of the spring coils.
 17. The connector according toclaim 13 wherein said spring is an axial spring having a back angle atan outside diameter of spring coils and a front angle on an insidediameter of the spring coils.
 18. The connector according to claim 1wherein said groove has a flat bottom.
 19. The connector according toclaim 1 wherein said groove has a V-bottom.
 20. The connector accordingto claim 1 wherein said groove has a tapered V-bottom groove.
 21. Theconnector according to claim 1 wherein said groove has a semi-taperedbottom.
 22. The connector according to claim 1 wherein said groove has around bottom with a shoulder therein.
 23. The connector according toclaim 1 wherein said groove has an inverted V-bottom.
 24. The connectoraccording to claim 1 wherein said groove has a V-bottom with differentangle subtending sides of said grooves.
 25. The connector according toclaim 1 wherein said groove is a dovetail groove.
 26. The connectoraccording to claim 1 wherein the groove is threaded.
 27. The connectoraccording to claim 26 wherein a groove width is smaller than a coilheight.
 28. The connector according to claim 1 further comprising aplurality of circular grooves formed in one of said bore and piston anda plurality of coil springs, one disposed in each of the grooves. 29.The connector according to claim 1 further comprising a plurality ofcoil springs disposed in the groove.
 30. The connector according toclaim 1 further comprising a elastomer disposed with said spring in saidgroove for providing both conductivity and environmental sealing. 31.The connector according to claim 30 wherein said elastomer coats coilsof said spring.
 32. The connector according to claim 30 wherein saidelastomer fills coils of said spring.
 33. The connector according toclaim 32 wherein said elastomer is solid.
 34. The connector according toclaim 32 wherein said elastomer has a hollow core.
 35. The connectoraccording to claim 32 wherein perimeters of the spring coils are notcovered by said elastomer.